Heating and cooling system



Nov. 29, 1966 L. H. LEOI\JIARD, JR 3,288,203

HEATING AND CO OLING SYSTEM Filed June 23, 1964 2 Sheets-Sheet l INVENTOR.

LOUIS H. LEONARD, JR.

BVWFM ATTORNEY.

Nov. 29, 1966 1.. H. LEONARD, JR

HEATING AND COOLING SYSTEM 2 Sheets-Sheet 2 Filed June 23, 1964 Y. m N 0 mm w mo in A E L H M s w 0 X .L

Y B 6 7 A\NO Two. M 8. 7 w u H m9 om a @0- M m u m N m v a u m m H L mo Fm United States Patent 3,288,203 HEATING AND COOLING SYSTEM Louis H. Leonard, Jr., Dewitt, N.Y., assignor to Carrier Corporation, Syracuse, N.Y., a corporation of Delaware Filed June 23, 1964, Ser. No. 377,319

. 15 Claims. (Cl. 165-2) This invention relates broadly to heating and cooling systems. More particularly, this invention relates to a capacity control for a heating and cooling system.

Various types of refrigeration systems, such as absorption systems and refrigerant compressor systems, are well known in the art. The construction, components and relative association of the components, as well as the operating characteristics of such systems are also well known. However, each system has certain disadvantages as well as particular advantages, but attempts to provide systems combining the advantages of accepted systems while avoiding their disadvantages have generally resulted in systems which were impractical.

For example, various expedients are known in the art for automatic-ally controlling the capacity of the various systems. In'systems utilizing a refrigerant compressor, such control is usually accomplished by varying the compressor speed or adjusting guide vanes in the compressor inlet to regulate the flow of refrigerant. Guide vane installations are expensive and generally require involved actuating mechanism. In systems which provide capacity control by regulating the compressor speed, this is commonly accomplished by controlling the speed of the compressor drive means, such as a steam turbine. Turbine speed control is generally obtained by varying the pressure of steam supplied to the turbine and this is usually accomplished either by varying the heat input to a steam generator or by adjusting a steam pressure regulating valve in the line between the steam generator and the turbine. Regulating the heat input to the steam generator usually results in poor capacity control because an inherently slow response of the steam generator causes the speed change of the turbine to lag behind the control signal varying the heat input to the steam generator, resulting in .slow change in the capacity of the system. When a steam pressure regulating valve is used, a significant pressure drop exists across the valve and this may result in an unnecessarily high steam rate, particularly at low steam pressures, producing higher operating costs. Furthermore, suitable steam pressure regulating valves are expensive and often require complicated and expensive electrical and mechanical actuating controls which increase the cost of the system. Another consideration is that of inherent instability of prior refrigeration system controls in that large, almost instantaneous changes in the operation of the system may occur for a variety of reasons, as is understood in the art.

Refrigeration systems which utilize a high speed centrifugal compressor and a relatively high molecular weight refrigerant are known to possess many theoretical advantages in size, cost and efficiency, as is more fully discussed in my prior copending United States patent application, Serial No. 112,679, filed May 25, 1961, for a Method and Apparatus for Heating and Cooling. However, practical problems affect the life and reliability of many such systems, and these problems have greatly increased the cost and complexity of the systems, so that early systems of this type have received little general acceptance.

Patented Nov. 29, 1966 "ice In three-pipe air conditioning installations, both cooling water and heating water are piped throughout the install-ation so that air circulating within the various areas can be regulated independently to a desired temperature. Asis generally understood, when the cooling demand throughout the installation is high, the cooling capacity of the system should greatly exceed the heating capacity,

and under reverse conditions, the heating capacity should greatly exceed the cooling capacity of the system. To vary the heating and cooling capacities of a system inversely of .eachother, as is desirable in a typical threepipe system, has required complicated and expensive controls, and many machines used for simultaneous heating and cooling are too delicate and easily become inoperative should leakage occur. Furthermore, prior machines have generally been unable to efficiently provide high heating capacity at low or zero cooling capacity I of such control by regulated blanketing of a condensing portion of a steam condenser employed in con-junction with the steam driven refrigeration system to suppress the condensing rate of steam discharged into the condenser. Another related object is provision for separating noncondensible vapor and steam mixed in the steam condenser, and returning the separated fluids for reuse in the system.

A further object is provision of a new and improved control system in a heating and cooling system for providing a stable system the normal operation of which changes slowly. A related object is provision of such control wherein the heating capacity varies inversely of the cooling capacity.

A still further object is provision of a new and improved heat exchanger. A related object is provision of such a heat exchanger for condensing a fluid, such as steam, in a system for providing heating and cooling. Another related object is provision of such a heat exchanger in the form of a steam condenser. Another related object is provision of a new and improved method of controlling the condensing rate of a condenser. Still another related object isprovision for controlled blanketing of a condensing portion of such a heat exchanger with a noncondensible vapor, preferably refrigerant vapor, to regulate the heating and condensing capacity of the heat exchanger. Still another related object is to provide an inexhaustable supply of the noncondensible vapor by recirculating the refrigerant providing the vapor. Another related object is provision of such a heat exchanger and method wherein a first condensing portion is blanketed with a noncondensible vapor and a second condensing portion is maintained effectively free of such blanketing to provide heat for a load to be heated.

A still further object is provision of a new and improved refrigeration system together with a method for providing simultaneous heating and cooling utilizing the improved refrigeration system. A related object is provision therein for varying the heating capacity inversely of the cooling capacity. Another related object is provision for extending the useful ranges of heating and cooling capacity.

Still anotherrelated object is provision of such a system and method which is particularly suited for use in a three pipe heating and cooling system.

A still further object is provision in a heating and cooling system of a new and improved method for controlling heating capacity inversely of cooling capacity.

These an other objects of the invention will be apparent from the following description and the accompanying drawings in which: 1

FIGURE 1 is a flow diagram of a heating and cooling system, and illustrates certain control features of the system;

FIGURE 2 is a broken, longitudinal side view of a condenser unit including a steam condenser of this invention, with parts :broken away for clearer illustration;

FIGURE 3 is a vertical sectional view of the condenser unit taken generally along the line IIIIII in FIGURE 2; and

FIGURE 4 is an end view from the right of the unit shown in FIGURE 2, with parts removed for clearer illustration.

The invention is illustrated in the form of apparatus, including a refrigeration apparatus for providing cooling, heating and simultaneous heating andcooling. The system is preferably airtight and may be considered as having a power side including a circuit for the circulation of a power fluid, and a refrigerant side including a circuit for the flow of a refrigerant fluid under the influence of drive means on the power side driven by the power fluid, with the operation of the apparatus regulated by a control system.

The invention will be described with reference to a preferred power fluid, which is water, and a preferred refrigerant which is octafluorocyclobutane, commonly referred to as C318 and having a chemical formula C F These fluids are particularly preferred because of their relative immiscibility and because they are inherently highly stable and do not tend to decompose or chemically react with each other or other materials in the system, or cause or promote corrosion and undesirable by-products. Also, this refrigerant is a relatively noncondensible vapor at the temperatures and pressure at which the power fluid (water) condenses as well as at the usual ambient atmospheric conditions of temperature and pressure. However, other power fluids and refrigerants having the desired chemical and physical properties may be utilized within the scope of this invention.

As illustrated in FIGURE 1, the power side includes a suitable steam generator 12 and a turbocompressor 13 including a turbine 14 which receives steam from the steam generator 12 and discharges exhaust steam to a steam condenser 16 here shown as part of a composite condensing unit as described in copending patent application of Joseph Embury for a Heat Exchanger Uni Serial No. 377,261 and filed on the same date the present application. A steam condensate pump 17 returns the steam condensate from the steam condenser 16 to the steam generator 12 for recirculation through the power side of the system. The turbocompressor 13 has water lubricated bearings, as 18, and the steam condensate pump 17 forwards steam condensate through a lubricant line 18' including a lubricant cooling heat exchanger 19, for lubricating the bearings 18.

The refrigerant side of the system includes a refrigerant compressor 20 of the turbocompressor 13. The compressor 20 is drivingly connected with the turbine 14 for passing compressed refrigerant vapor to a refrigerant condenser 21 here shown as part of composite condensing unit, although a separate structure may be employed if desired to condense the refrigerant. Condensed refrigerant passes from the refrigerant condenser 21 to a refrigerant subcooler 22 and through a suitable refrigerant flow restricting means 23 into an evaporator or cooler 24, from which the refrigerant vapor is withdrawn by the refrigerant compressor 20, thus completing the refrigerant circuit of the system. A chilled water line 25 extends into the cooler and carries a heat exchange medium here in the form of chilled water, which is cooled by the refrigerant and circulated by means of a chilled water pump 26 to an area having a cooling requirement. The cooling capacity of the system varies in proportion to the compressor output.

A cooling tower or condensing water pump 27 circulates tower water through an inlet line 28 to the refrigerant subcooler 22 and into the refrigerant condenser 21 and then the steam condenser 16 and back to the tower through an outlet line 29. A branch line 30 in the condensing water inlet line 28 provides tower water to the lubricant water cooler 19 for cooling the lubricant water, and this branch terminates in the return line 29 to the tower. In general, control of condensing water temperature and flow rate is unnecessary, thus effectively minimizing scaling of condensing surfaces in the condensers.

The control system regulates the cooling and heating capacities of the refrigeration system by varying the steam condenser pressure as determined by the condensing rate of steam discharged into the steam condenser.

In my copending United States patent application for a Refrigeration System, Serial No. 377,313, and filed on the same date as the present application, cooling capacity control of the present system is more fully described. In brief, the condensing rate of the steam condenser is regulated by controlled blanketing of a first condensing portion or tube bundle 34 (which receives the tower water from the refrigerant condenser) with a noncondensible vapor, herein refrigerant vapor, introduced through a refrigerant line 34' from the cooler 24.

The quantity of noncondensible vapor effectively blanketing the first condensing portion 34 of the steam condenser is regulated by a modulating refrigerant valve 35 in the line 34. The valve 35 is actuated responsive to chilled water temperature by means of a temperature sensor 37 on the chilled water line 25 so that as the cooling load drops more refrigerant vapor is introduced into the steam condenser 16 thus reducing the steam condensing rate to increase the steam condenser pressure, and therefore the temperature of the saturated steam and the turbine discharge pressure to reduced the turbocompressor output and in general speed. The refrigerant is preferably withdrawn from the steam condenser at a constant rate, and herein a water supply pump 38 circulates impeller water for operating a jet pump 39 which withdraws the noncondensible vapor from the steam condenser 16 through a purge line 40 opening into the throat of the jet pump. Impeller water temperature is maintained below the saturation temperature of water in the steam condenser to prevent water from flashing in the jet pump 39, and to this end, the hot vapors withdrawn from the steam condenser are cooled in the cooler 24. The water supply pump 38 further provides make-up water for the steam generator 12 through a make-up water line 40' to the steam condenser 16.

Simultaneous heating and cooling, wherein the heating and cooling capacities of the system vary inversely of each other, is provided. A second condensing portion or tube bundle 41 in the steam condenser is maintained effectively free of blanketing by refrigerant vapor in the steam condenser to maintain its full condensing capacity and maximum heating of a heat exchange medium, herein water, circulated through the bundle 41 and to a load to be heated by means of a heating water pump 41' in a heating line 41" to the area having a heating requirement. Thus, at high cooling capacity only a small quantity of refrigerant is in the steam condenser to blanket the first condensing portion 34 and the condensing rate is high so that the steam condenser pressure is'low and the temperature of saturated steam in the condenser is correspondingly low. Therefore, the temperature of the water in the second condensing portion-41 is low and little heat is provided for the load to be heated. Conversely, when the cooling capacity is low the heating capacity is high, and the temperature of the heating water is at high, useable temperatures.

A hot gas bypass for increasing the heating capacity of the system at low cooling capacity, agitating the refrigerant entering the cooler to provide improved heat transfer to the chilled water line at low cooling capacity, and for effectively preventing compressor surge, includes a hot gas bypass line 42 for passing refrigerant gas from the refrigerant condenser 21 to the cooler 24. Operation of the bypass is controlled by a self-contained modulating refrigerant valve 42' which is operated responsive to steam condenser condition and, more particularly, by steam condenser pressure as determined by a valve pressure sensor 42" in the steam condenser 16. Alternatively, the valve 42 may be controlled responsive to steam condenser or turbine discharge steam temperatures which are equivalent to steam condenser pressure in view of existing saturated steam condition. Blanketing of the steam condenser first tube bundle 34 with refrigerant vapor can be expected to provide partial load operation down to about 50% of nominal full load cooling capacity. Without the hot gas bypass, the compressor would then go into surge and the machine would have to be shut down. As the compressor approaches surge condition, the heating capacity will increase in inverse proportion to the cooling capacity. By using the hot gas bypass for effectively preventing compressor surge, substantially zero cooling capacity can be provided and the heating capacity increased simultaneously to about 75% of the nominal maximum winter heating capacity of the machine, and at useable heating water temperature levels. As the hot gas bypass 42 loads the compressor 20, the turbine 14 utilizes a greater quantity of steam to drive the compressor. Upon fully opening the hot gas bypass valve the compressor is loaded to the extent that no useful cooling is provided by the cooler 24. While the steam condenser pressure rises slightly because of the greater volume of entering steam during such loading, and therefore the temperature of the entering steam rises only slightly, the increased volume of steam provides a substantially increased source of heat for heating the second tube bundle 41, thereby increasing the heating capacity of the heating and cooling system. Thus, the suitability of the machine for operation in conjunction with threepipe systems is greatly enhanced.

To provide cooling without heating, the heating water pump 41 may be turned off. It should be noted that all pumps are preferably self-lubricated by water being pumped therethro-ugh.

If it is desired to provide only heating, as for winter heating, the condensing water ptunp 27 may be shut off and valve means 43 in the steam line to the turbocompressor 13 may be adjusted so that the steam bypasses the turbine 14 and is injected directly into the steam condenser 16 for heating the second condensing portion 41. A heat exchanger 43' may be provided for cooling the jet impeller water circulated by the pump 38, to maintain the impeller water below the saturation temperature of water in the steam condenser to prevent water from flashing in the jet pump and rendering the purge inoperative.

In the illustrated apparatus the steam generator 12 supplies steam at a substantially constant pressure (15 p.s.i.g., for example) as controlled for example, by a constant pressure regulating valve 50 in a steam supply line 51 to the turbine and including the valve means 43. By merely changing the internal design of the steam turbine section of the turbocompressor, the machine may be operated with any normally desired steam pressure.

As is more fully describd in my copending United States patent application for a Heating and Cooling System, Serial No. 377,258, and filed on the same date as the present application, steam drives a turbocompressor rotor assembly 55 which is rotatably mounted in the turbocompressor housing '56 by means of the water lubricated bearings 18. From the bearings 18 the lubricating water passes into a chamber 73 generally in the center of the housing 55. Suitable shaft seals, as 75, one at either end of the portion of the housing 56 mounting the shaft, minimize leakage of steam and refrigerant between the turbine and the compressor and any leakage passes into the chamber 73 from which the lubricating water and leakage pass through a drain line 76 to the steam condenser 16.

With particular reference to FIGURES 2-4, after passing the turbine rotor, the steam is saturated and passes through a turbine steam discharge passage 81 and into the steam condenser 16. More particularly, with reference to FIGURE 2, the turbocompressor 13 is suitably mounted on an end plate 82 of the steam condenser, as by bolts, with the turbine discharge passage in communication with a steam inlet port 84 in the end plate. A- condensate chamber 86 of the steam condenser 16 is in communication with the interior of a cylindrical shell 87 of the steam condenser 16 through a port 88 in the end wall plate 82. The turbocompressor drain 76 opens into the condensate chamber 86. The steam condensate pump 17 withdraws the steam condensate from the condensate chamber through a condensate line 103 and pumps the condensate back to the steam generator 12. Thus, the turbocompressor chamber 73, the steam discharge passage 81, the drain 76, and the interior of the steam condenser 16, are all at substantially the same pressure, that is, the steam condenser pressure which is below ambient atmospheric pressure during normal operation.

Within the steam condenser shell 87, both the first condensing bundle 34 and the second condensing bundle 41 may be of any suitable type such as straight through tubes, or as illustrated, U-tubes secured in and open through a header plate 101 opposite the end plate 82. A header chamber shell 102 is suitably secured to the header plate 101, as by bolts 102', and has partitions, as 102", for circulating condensing water from the refrigerant condenser through the U-tubes of the first condensing portion 34 and then discharging the condensing water through the condensing water outlet line 29 to the cooling tower. Inlet and outlet branches of the heating water line 41" open into the header 102'and suitable communication is provided by means of the shell partitions 102" with the U-tubes of the second condensing portion 41 to provide water for condensing steam and for returning the heated water to the area having a heating requirement.

The refrigerant injected into the steam condenser to blanket the first condensing portion 34 enters the steam condense-r through a refrigerant port 106 at the end of the refrigerant line 34' within the steam condenser 16 between the first condensing tube bundle 34 and the second condensing tube bundle 41 adjacent an end of the condensing tubes opposite the condensate port 88 and the steam inlet 84, as may best be seen in FIGURE 2.

A baffle 107 (FIGURES l-3) extends between upper and lower 'portions'of the steam condenser between the first and second condensing tube bundles 34 and 41, to define a condensate section and another section, respectively, and to prevent the flow offluids the rebetween except in a limited area of communication 108 at the refrigerant port 106. The entering steam first flows from the steam condenser inlet port 84 across the second condensing b-undle 41 and then through the area of limited communication 108 between the upper and lower sections of the steam condenser and past the refrigerant inlet port 106, and then past the first condensing bundle 34. The refrigerant vapor entering the steam condenser 16 is drawn across the tubes of the first condensing bundle 34, and in the illustrated embodiment each tube is effectively individually enveloped by a sheath or layer of refrigerant vapor thereby insulating the tubes of the first condensing bundle from the steam to reduce the steam condensing capacity and the system cooling capacity while raising the pressure and temperature of the saturated steam in the condenser to raise the systems heating capacity by providing more heat for rejection by bundle 41.

With reference to FIGURES 2 and 4, the purge line 40 opens into a side of the steam condensate chamber 86 at a level to withdraw steam condensate from the chamber should the condensate level rise too high. Responsive to .a 'low condensate level in the condensate chamber 86, a float actuated sens-or 112 opens a normally closed shutoff valve 113 in the snake-up water line 40 from the water supply pump 38, to maintain a minimum level of condensate in the chamber 86.

In the ilustrated embodiment, a cylindrical refrigerant condenser shell 116 extends between the condenser end plate 82 and the header plate 101 and envelopes the steam condenser shell 87 for effectively preventing leakage of air into the steam condenser and to insulate the steam condense-r for winter heating. Suitable U-tubes, as 117, are provided in the refrigerant condenser and have adjacent ends suitably mounted in and opening through the header plate 101 in communication with partitioned areas of the header chamber shell 102 so that condensing water from the refrigerant subcooler 22 is first circulated through the refrigerant condenser U-tubes 117 and then passed through the tubes of the steam condenser first condensing bundle 34 before being discharged from the condensing unit through the condensing water outlet 29.

Responsive to the compressor 20 being drive-n by the turbine 14, refrigerant vapor is withdrawn from the cooler 24 through a suction line 121 to the compressor inlet, compressed, and discharged through a compressor outlet and a discharge line 122 into the refrigerant condenser 21 where it is condensed and cooled. The refrigerant condensate then flows through a refrigerant condensate line 123 into the refrigerant su bcooler 22 from which it passes through the refrigerant flow restricting means 23, here in the form of a float valve unit, and flows through a cooler refrigerant supply line 124 and into a cooler refrigerant inlet 125 extending through :a shell 126 of the cooler 24. A suitable equalizer line 126' connects the float valuve unit chamber and the refrigerant condenser, forreasons well understood in the art.

The refrigerant inlet 125 opens into a refrigerant pan 127 spaced above the bottom of the cooler shell 126. A U-tube bundle 128 of the chilled water line 25 is within the refrigerant pan 127 so that during normal cooling operation of the system, the tubes are flooded by boiling refrigerant. As the refrigerant evaporates, the vapor passes into a refrigerant chamber 129 in an upper portion of the cooler shell 126 above the pan and the remaining liquid refrigerant is cooled thereby. A refrigerant outlet 130 opens into an upper portion of the refrigerant chamber 129 and is connected with the compressor inlet 120 by the suction line 121. The portion of the cooler 24 below the refrigerant pan 127 provides a water sump 132 which contains the jet pump 39 so that the impeller water and refrigerant and any water vapors purged from the steam condenser 16 are injected into the sump 132 and sum-p water is withdrawn from the sump through a pump supply line 133 so that the sump water is recirculated through the sump. During normal cooling operation of the system, the sump is maintained at least F. above the temperature of the refrigerant chamber, so that refrigerant in the sump is a vapor which passes upwardly about the left end of the refrigerant pan 127 and into the refrigerant chamber 129 from which it is withdrawn through the suction line 121. Water in the re frigerant chamber 129 collects on top of the liquid refrigerant in the pan 127. The chilled water tube bundle 128 is spaced inwardly from the left end wall of the pan to form a relatively quiet area of liquid refrigerant upon which :any Water in the pan collects in a relatively quiet pool and flows through a suitable weir or port 134 in .the end of the pan and into the sump 132. Thus, means is provided for separating refrigerant fluid and power fluid, and for returning these fluids for reuse in the system.

To summarize the operation of the system, if the chilled Water temperature drops, indicating a reduced cooling requirement, the modulating refrigerant valve 35 in the refrigerant line 34 to the steam condenser 16 is opened additionally to permit more refrigerant to enter the steam condenser for blanketing the first condensing bundle 34 to reduce the steam condensing capacity and increase steam condenser pressure and the turbine discharge pressure, thus slowing the turbocompressor and causing the compressor 20 to deliver a smaller quantity of refrigerant to the cooler 24, thereby reducing the cooling ca pacity of the system and increasing the temperature of the leaving chilled water. The pressure and temperature of the steam in the condenser are increased, thus increasing the heating capacity of the second tube bundle 41. Should the chilled water temperature rise, indicating a rise in the cooling requirement, the refrigerant valve 35 is closed sulficiently and less refrigerant is injected into the steam condenser so that the quantity of refrigerant vapor effectively blanketing the first condensing bundle 34 is reduced as the constant rate purge withdraws refrigerant from the steam condenser, thus increasing the cooling capacity and reducing the heating capacity of the system. If desired, suitable guide vanes may be provided on the compressor to improve efliciency somewhat, as is understood in the art.

The following chart, indicates various cooling operation conditions throughout the system.

Cooling Capacity 50% 0% Entering Condensing Water,

F 85 65 85 65 85 65 Lv.1Chilled Water, F 44 43 42 41. 5 40. 5 40 36 35 34 33 32. 5 32 19. 7 19. 2 18. 7 l8. 2 l8 l7. 7

130 135 P.s.i.a 1. 5 4. 2 2. 2 6. 7 2. 5 7. 5 Ref. Condenser:

F 105 85 95 75 86 66 P.s.i.a 70 51 60 43 52 36 Ref. Leaving Subcooler, F. 95 75 90 7O 86 66 The invention provides a low first cost installation over a wide range of capacities, and small leaks will not render the machine completely inoperative. The machine is completely and truly airtight and routine service requirements are virtually nonexistent, for example, the machine does not require periodic additions of capacity restorer, nor are alkalinity checks required as with most absorption machines.

In the present system, the boiler need never be descaled since no make-up water need be added to the machine. By simpler changeover in the turbocompressor, a high steam pressure machine can easily be converted into a low pressure machine, in case operator license requirement'becomes important. High partial load efliciency may be obtained by directly modulating boiler input and by the use of refrigerant compressor inlet guide vanes.

Because the steam condenser condensing rate is regulated by blanketing, control of entering condensing waterv temperatures and flow rate is unnecessary, so that lower average condensing Water temperatures may be utilized for greatly reducing operating costs and effectively preventing scaling. Furthermore, the system completely eliminates condensing or absorbent condensing water bypass lines and valves as are used on most absorption machines and also eliminates the need for sensitive condensing water flow adjustment.

While a preferred embodiment of the invention has been described and illustrated, it will be understood that the invention is not limited thereto since it may be otherwise embodied within the scope of the following claims.

I claim:

1. A method of operating a simultaneous heating and cooling system including a turbine driven refrigerant compressor and a steam condenser having first and second condensing portions, comprising the steps of supplying substantially constant pressure steam to the turbine for driving the turbine, supplying to the condenser the steam discharged from the turbine, blanketing at least a portion of the first condensing portion with refrigerant vapor for reducing its condensing capacity to increase the steam temperature in the condenser and the heating capacity of the second portion and to increase the discharge pressure of the turbine thereby reducing the turbine and compressor outputs below their maximum outputs to reduce the cooling capacity of the system, and regulating the quantity of said refrigerant vapor blanketing the first condensing portion for regulating the steam temperature and the discharge pressure on the turbine to vary the capacities of the system.

2. A method according to claim 1 including the steps of withdrawing refrigerant vapor and any water vapor carried thereby from said condenser, separating the withdrawn fluids, and returning the separated fluids for reuse in the system.

3. A method according to claim 1 including the steps of introducing refrigerant, Withdrawing said refrigerant vapor from the first condensing portion of said condenser at a substantially constant rate, and regulating the rate of introducing said refrigerant into said condenser in response to cooling load imposed upon the system.

4. A method of operating a simultaneous heating and cooling system including a turbine driven refrigerant compressor and a power vapor condenser, comprising the steps of supplying power vapor to the turbine for driving the turbine, supplying to the condenser the power vapor discharged from the turbine, removing heat from the power vapor in the condenser to satisfy a heating requirement, mixing refrigerant vapor with the confined power vapor in said condenser for increasing the discharge pressure of the turbine and increasing the power vapor temperature thereby reducing the turbine and compressor outputs below their maximum outputs to reduce the cooling capacity and increase the heating capacity of the system, and regulating the quantity of refrigerant mixed with said confined power fluid to regulate said capacities.

5. In a heating and cooling system utilizing steam power fluid and a refrigerant fluid the combination of a refrigerant compressor, drive means for receiving steam power fluid to drive the compressor, a steam condenser for receiving discharge steam from said drive means, said steam condenser including first condensing means to condense the steam and reject the heat involved therein and second condensing means to condense steam and conserve the heat involved therein for supply to a load to be heated, means for blanketing said first condensing means with refrigerant vapor to limit the steam condensing capacity thereof and for maintaining said second condensing means effectively free of said refrigerant to provide substantially maximum heating thereof, thereby increasing the steam condenser pressure and temperature to reduce the output of the compressor and the cooling capacity of the system and to increase the heating capacity of the system, and control means for regulating the blanketing of said first condensing means to control said capacities.

6. A system according to claim 5 in which said control means are responsive to the load imposed on the system.

7. A system according to claim 5 which includes a cooler, a chilled water line associated with said cooler for circulating chilled water to a load to be cooled, and said control means being responsive to the temperature of said chilled water.

8. A system according to claim 5 in which means are provided for the heating capacity of the system at low 10 cooling capacity by loading the compressor with heated refrigerant vapor for effectively preventing compressor surge at low cooling capacity without substantially affecting heating capacity of the system.

9. A system according to claim 5 in which a hot gas bypass is provided operable responsive to steam condenser condition to load the compressor with hot refrigerant gas for effectively preventing compressor surge.

10. In a heating and cooling system utilizing steam power fluid and a refrigerant fluid the combination of steam supply means, a refrigerant compressor, drive means connected with said steam supply means for receiving steam po-wer fluid to drive the compressor, a steam condenser connected with said drive means for receiving discharge steam from said drive means, said steam condenser including first condensing means to condense the steam and reject the heat involved therein and second condensing means to condense steam and conserve the heat involved therein for supply to a load to be heated, means for passing steam condensate from said steam condenser to said steam supply means, blanketing means for blanketing at least a portion of said first condensing means with refrigerant vapor to limit the steam con-densing capacity thereof and for maintaining said second condensing means effectively free of said refrigerant to provide substantially maximum heating thereof, thereby increasing the steam condenser pressure and temperature to reduce the output of the compressor and the cooling capacity of the system and to increase the heating capacity of the system, control means for regulating the blanketing of said first condensing means to control said capacities, and means for bypassing said drive means and providing direct communication between said steam supply means and said steam condenser, thereby rendering said compressor inoperative for cooling, while providing heat to the load to be heated.

11. In a heating and cooling system utilizing steam power fluid and a refrigerant fluid immiscible with and having a lower boiling point than the power fluid the combination of steam supply means on a power side of the system, a turbocompressor including a refrigerant compressor and a turbine connected for receiving steam power fluid from said supply means to drive the compressor, a steam condenser having a steam inlet connected with said turbine for receiving discharge steam from said turbine, said steam condenser including first condensing means to condense the steam and reject the heat involved therein and second condensing means apart from said first condensing means to condense steam and conserve the heat involve-d therein for supply to a load to be heated, means for returning stream condensate from said steam condenser to said steam supply means, blanketing means for passing refrigerant into said steam condenser and blanketing said first condensing means with said refrigerant to limit the steam condensing capacity thereof and thereby the output of the turbine and the cooling capacity of the system while directing said refrigerant away from said second condensing means so that said second condensing means is effectively free of said refrigerant to provide substantially maxim-um heating thereof, means for withdrawing refrigerant fluid and any water vapor carried thereby from said steam condenser, and control means for regulating the blanketing of said first condensing means to control operation of the system.

12. In the system of claim 11, said blanketing means comprising, a baflie between said first condensing means and said second condensing means dividing said steam condenser into a condensate section and another section, respectively, and providing a limited area of communication between said sections proximate an end of said steam condenser, the steam condenser steam inlet being spaced from said area and opening into the other section, whereby steam to be condensed first passes over said second condensing mean-s and then over said first condensing means so that upon increasing the blanketing of said first condensing means with refrigerant to reduce the system cooling capacity, the system heating capacity increases.

13. In the system of claim 12, said blanketing means passing refrigerant into said steam condenser at said limited area of communication between said section, whereby refrigerant vapor is concentrated in said condensate section to blanket said first condensing means.

14. The system of claim 13 wherein said blanketing means for withdrawing refrigerant fluid includes purge means opening into a portion of said condensate section remote from said area.

15. A method according to claim 4 including the step of reducing the cooling capacity by loading the compressor with refrigerant vapor for effectively preventing compressor surge.

References Cited by the Examiner UNITED STATES PATENTS 2,830,797 4/1918 Garland 165146 3,153,442 10/1964 Silvern 16550 3,204,692 9/1965 Smith 1651 10 10 ROBERT A. OLEARY, Primary Examiner.

C. SULKALO, Assistant Examiner.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3,288,203 November 29, 1966 Louis H. Leonard, Jr.

It is hereby certified that error appears in the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

Column 3, line 7, for "an" read and line 54, after "date" insert as column 4, line 42, for "reduced" read reduce column 7, line 42, for "valuve" read valve column 8, line 56, for "simpler" read simple column 9,

line 75 and column 10, line 1, strike out "the heating capacity of the system at low cooling capacity by".

Signed and sealed this 19th day of September 1967.

(SEAL) Attest:

ERNEST W. SW'IDER EDWARD J. BRENNER Attesting Officer I Commissioner of Patents 

1. A METHOD OF OPERATING A SIMULTANEOUS HEATING AND COOLING SYSTEM INCLUDING A TURBINE DRIVEN REFRIGERANT COMPRESSOR AND A STEAM CONDENSER HAVING FIRST AND SECOND CONDENSING PORTIONS, COMPRISING THE STEPS OF SUPPLYING SUBSTANTIALLY CONSTANT PRESSURE STEAM TO THE TURBINE FOR DRIVING THE TURBINE, SUPPLYING TO THE CONDENSER THE STEAM DISCHARGED FROM THE TURBINE, BLANKETING AT LEAST A PORTION OF THE FIRST CONDENSING PORTION WITH REFRIGERANT VAPOR FOR REDUCING ITS CONDENSING CAPACITY TO INCREASE THE STEAM THE TEMPERATURE IN THE CONDENSER AND THE HEATING CAPACITY OF THE SECOND PORTION AND TO INCREASE THE DISCHARGE PRESSURE OF THE TURBINE THEREBY REDUCING THE TURBINE AND COMPRESSOR OUTPUTS BELOW THEIR MAXIMUM OUTPUTS TO REDUCE THE COOLING CAPACITY OF THE SYSTEM, AND REGULATING THE QUANTITY OF SAID REFRIGERANT VAPOR BLANKETING THE FIRST CONDENSING PORTION FOR REGULATING THE TEAM TEMPERATURE AND THE DISCHARGE PRESSURE ON THE TURBINE TO VARY THE CAPACITIES OF THE SYSTEM. 